CN102491173A - Crane and closed type winch negative power control system for crane - Google Patents
Crane and closed type winch negative power control system for crane Download PDFInfo
- Publication number
- CN102491173A CN102491173A CN2011104122150A CN201110412215A CN102491173A CN 102491173 A CN102491173 A CN 102491173A CN 2011104122150 A CN2011104122150 A CN 2011104122150A CN 201110412215 A CN201110412215 A CN 201110412215A CN 102491173 A CN102491173 A CN 102491173A
- Authority
- CN
- China
- Prior art keywords
- valve
- proportional reversing
- control
- negative power
- gear box
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000003638 chemical reducing agent Substances 0.000 claims abstract description 5
- 239000012530 fluid Substances 0.000 claims description 21
- 230000007246 mechanism Effects 0.000 claims description 5
- 238000012546 transfer Methods 0.000 abstract description 7
- 230000000694 effects Effects 0.000 abstract description 6
- 238000000034 method Methods 0.000 description 12
- 238000010521 absorption reaction Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 4
- 230000006870 function Effects 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 3
- 239000000446 fuel Substances 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000002745 absorbent Effects 0.000 description 1
- 239000002250 absorbent Substances 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000005055 memory storage Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
- 238000012797 qualification Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
- B66C13/20—Control systems or devices for non-electric drives
Landscapes
- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Mechanical Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Control And Safety Of Cranes (AREA)
Abstract
The invention provides a crane and a closed type hoisting negative power control system for the crane, which are used for solving the problem of poor effect of closed type hoisting negative power control for the crane in the prior art. This control system includes engine, transfer case, open system, and closed system, wherein: the open system and the closed system are respectively connected with the transfer case and are connected to the engine through the transfer case; the closed system comprises a closed variable pump connected with the transfer case, a hoisting motor connected with the closed variable pump through a hydraulic pipeline, and a hoisting speed reducer connected with the hoisting motor; the transfer case is used for transmitting part or all of negative power to the open system when the crane performs descending operation. By applying the technical scheme of the invention, the negative power generated when the closed type winch descends is transmitted to the open type system by the transfer case and absorbed by the open type system, and the descending speed of the heavy object is not limited any more, so that the closed type winch has better control effect.
Description
Technical field
The present invention relates to technical field of engineering machinery, relate to a kind of hoisting crane and hoisting crane especially with enclosed elevator negative power control system.
Background technology
Hoisting crane is a kind of common construction machinery and equipment.In the correlation technique, to realize hoisting of lift heavy thing, mainly comprise controllable capacity pump and hoist motor in this closed system by engine drive open type or closed system.
The speed that weight descends in open-circuit system can be come regulating control through balance cock, and poor because of the closed system radiating effect in closed system, therefore balance cock can not be installed.Negative power absorption pattern in the correlation technique mainly absorbs a part of negative power through driving engine itself, and its principle is as shown in Figure 1.Fig. 1 is according to the scheme drawing of the hoisting crane in the correlation technique with enclosed elevator negative power absorption pattern principle.Arrow among Fig. 1 is represented the flow of power, and weight G is the lift heavy thing of hoisting crane.As shown in Figure 1, weight G produces negative power when descending, and this negative power passes to closed system, and closed system is to engine output, correspondingly the driving engine absorbed power.
In the correlation technique, can only limit the generation of negative power through the descending speed of restriction weight.Development along with the hoisting crane industry; Hoisting capacity is increasing; The negative power that need absorb during decline also more and more (because the size and the weight quality of negative power are directly proportional); Speed is confined also more and more littler, because of the absorbent negative power of driving engine itself is limited, has driving danger after exceeding the absorption region of driving engine.Therefore the poor effect of controlling with enclosed elevator negative power for hoisting crane in the correlation technique for this problem, does not propose effective solution as yet in the correlation technique.
Summary of the invention
Main purpose of the present invention provides a kind of hoisting crane and hoisting crane with enclosed elevator negative power control system, to solve in the prior art problem of the poor effect of controlling with enclosed elevator negative power for hoisting crane.
To achieve these goals, according to an aspect of the present invention, provide a kind of hoisting crane with enclosed elevator negative power control system.
Hoisting crane of the present invention is used to absorb the negative power that the hoisting mechanism of hoisting crane produces with enclosed elevator negative power control system when the lift heavy thing is transferred; Said control system comprises driving engine, auxiliary gear box, open-circuit system and closed system; Wherein: said open-circuit system is connected with said auxiliary gear box respectively with closed system, and is connected to said driving engine through said auxiliary gear box; Said closed system comprise with said auxiliary gear box bonded assembly enclosed controllable capacity pump, through hydraulic tubing and said enclosed controllable capacity pump bonded assembly hoist motor and with said hoist motor bonded assembly hoisting speed reducer; Said auxiliary gear box is used for when hoisting crane descends operation said negative power partly or entirely passed to said open-circuit system.
Further, comprise in the said open-circuit system: the open type controllable capacity pump, be connected with said auxiliary gear box, be used for obtaining power and pressure oil output from said auxiliary gear box; Proportional reversing valve is connected with said open type controllable capacity pump; The loading by pass valve of said hoisting crane is connected with said proportional reversing valve; The guide proportion reducing valve is connected with said proportional reversing valve, is used to control said pressure oil flows to said loading by pass valve via said proportional reversing valve flow.
Further, comprise in the said open-circuit system: the open type controllable capacity pump, be connected with said auxiliary gear box, be used for obtaining power and pressure oil output from said auxiliary gear box; Pilot operated directional control valve is connected with said open type controllable capacity pump; Ratio loads by pass valve, is connected with said pilot operated directional control valve; Solenoid directional control valve is connected with said pilot operated directional control valve, is used to control the conducting of said pilot operated directional control valve or turn-off.
Further, comprise in the said open-circuit system: the open type controllable capacity pump, be connected with said auxiliary gear box, be used for obtaining power and pressure oil output from said auxiliary gear box; First and second proportional reversing valves all are connected with said open type controllable capacity pump; First to fourth guide proportion reducing valve, wherein the first and second guide proportion reducing valves are connected with first proportional reversing valve, and the third and fourth guide proportion reducing valve is connected with second proportional reversing valve; Hydraulic Elements and loading by pass valve, first hydraulic fluid port of wherein said Hydraulic Elements is connected with said first and second proportional reversing valves, and second hydraulic fluid port is connected with said second proportional reversing valve, and said loading by pass valve is connected with said second proportional reversing valve; And said Hydraulic Elements are used to absorb the power that said open type controllable capacity pump is obtained; The said first guide proportion reducing valve is used to control said pressure oil flows to first hydraulic fluid port of said Hydraulic Elements via said first proportional reversing valve flow; The said second guide proportion reducing valve is used to control said pressure oil flows to second hydraulic fluid port of said Hydraulic Elements via said first proportional reversing valve flow; Said the 3rd guide proportion reducing valve is used to control said pressure oil flows to first hydraulic fluid port of said Hydraulic Elements via said second proportional reversing valve flow; Said the 4th guide proportion reducing valve is used to control said pressure oil flows to said loading by pass valve via said second proportional reversing valve flow.
Further, said loading by pass valve is that ratio loads by pass valve.
Further, said Hydraulic Elements are the HM Hydraulic Motor of two plate valves interflow control or the telescopic oil cylinder of two plate valves interflow control.
Further, said Hydraulic Elements are the amplitude oil cylinder of said hoisting crane, and said first hydraulic fluid port is the rodless cavity of this amplitude oil cylinder, and said second hydraulic fluid port is the rod chamber of this amplitude oil cylinder.
Further, said amplitude oil cylinder is two amplitude oil cylinder.
Further, said open type controllable capacity pump is load sensing pump or automatically controlled controllable capacity pump.
According to another aspect of the invention, a kind of hoisting crane is provided, this hoisting crane comprises that hoisting crane of the present invention is with enclosed elevator negative power control system.
Use technical scheme of the present invention, can obtain following beneficial effect:
The negative power that is produced when 1, the enclosed elevator descends is delivered to open-circuit system by auxiliary gear box, is absorbed by open-circuit system, and the weight descending speed no longer is restricted;
2, realize that through the electric current of control guide proportion reducing valve proportional reversing valve exports to the flow proportional control that ratio loads by pass valve; Load the different loading power of by pass valve to obtain ratio; Owing to be controlled to be step-less adjustment, therefore load and stablize, can not make speed produce sudden change;
But 3, the ratio also step-less adjustment of pressure that loads by pass valve, the low system overshoot of hour setting pressure is little for the negative power that produces in closed system, loads more steadily, and the negative power that produces when closed system is greatly the time, the higher satisfied loading power requirement of setting pressure;
4, how the negative power that no matter closed system is exported changes, and the pressure that all can load by pass valve through the electric current or the ratio of control guide proportion reducing valve make the power of driving engine maintain target control value;
5, realize amplitude-variation hoisting and two functions of system loads by a proportional reversing valve, more traditional mode has been saved a proportional reversing valve.
Description of drawings
Figure of description is used to provide further understanding of the present invention, constitutes the application's a part, and illustrative examples of the present invention and explanation thereof are used to explain the present invention, do not constitute improper qualification of the present invention.In the accompanying drawings:
Fig. 1 is according to the scheme drawing of the hoisting crane in the correlation technique with enclosed elevator negative power absorption pattern principle;
Fig. 2 is the scheme drawing of the power transitive relation during according to the engine output of the embodiment of the invention;
Fig. 3 is the scheme drawing of the power transitive relation during according to the driving engine absorbed power of the embodiment of the invention;
Fig. 4 is according to the hoisting crane of the embodiment of the invention first kind of basic structure scheme drawing with enclosed elevator negative power control system;
Fig. 5 is according to the hoisting crane of the embodiment of the invention second kind of basic structure scheme drawing with enclosed elevator negative power control system;
Fig. 6 is according to the hoisting crane of the embodiment of the invention the third basic structure scheme drawing with enclosed elevator negative power control system;
Fig. 7 is according to the hoisting crane of the embodiment of the invention the 4th kind of basic structure scheme drawing with enclosed elevator negative power control system.
The specific embodiment
Need to prove that under the situation of not conflicting, embodiment and the characteristic among the embodiment among the application can make up each other.Below with reference to accompanying drawing and combine embodiment to specify the present invention.
The hoisting crane of the embodiment of the invention is mainly used in the negative power that the hoisting mechanism that absorbs hoisting crane produces with enclosed elevator negative power control system when the lift heavy thing is transferred.Fig. 2 is the scheme drawing of the power transitive relation during according to the engine output of the embodiment of the invention.Fig. 3 is the scheme drawing of the power transitive relation during according to the driving engine absorbed power of the embodiment of the invention.
As shown in Figures 2 and 3, the hoisting crane of the embodiment of the invention mainly comprises driving engine 1, auxiliary gear box 2, open-circuit system 3 and closed system 4 with enclosed elevator negative power control system.Wherein open-circuit system 3 is connected with auxiliary gear box 2 respectively with closed system 4, and is connected to driving engine 1 through auxiliary gear box 2.Closed system 4 comprises interconnective enclosed controllable capacity pump and hoist motor, also comprises the hoisting speed reducer (not shown).Auxiliary gear box 2 can be used in when hoisting crane rises operation power with driving engine output, and to pass to open-circuit system 3 (as shown in Figure 3 with closed system 4; Wherein arrow is represented power flow direction); Control aspect for negative power; Auxiliary gear box 2 can be when hoisting crane descends operation with the part of negative power (this moment, another part passed to driving engine) or all pass to open-circuit system 3 (as shown in Figure 3, wherein arrow is represented power flow direction).Fig. 3 also shows weight G, and this weight G produces negative power when descending.
Fig. 4 is according to the hoisting crane of the embodiment of the invention first kind of basic structure scheme drawing with enclosed elevator negative power control system.As shown in Figure 4, hoisting crane is to comprise with first kind of optional structure of the open-circuit system 3 in the enclosed elevator negative power control system: open type controllable capacity pump 30, be connected with auxiliary gear box 2, and be used for obtaining power and pressure oil output from auxiliary gear box; Proportional reversing valve 41; The loading by pass valve 43 of guide proportion reducing valve 42, hoisting crane.And open type controllable capacity pump 30, guide proportion reducing valve 42 and loading by pass valve 43 are connected with proportional reversing valve 41 respectively; Guide proportion reducing valve 42 is used for control presssure oil and flows to the flow that loads by pass valve 43 via proportional reversing valve 41.Proportional reversing valve 41 has been shown in Fig. 4 has taked the situation of three proportional reversing valve, can block the B1 mouth this moment, as shown in Figure 4; Also can adopt two proportional reversing valve in addition.
Fig. 5 is according to the hoisting crane of the embodiment of the invention second kind of basic structure scheme drawing with enclosed elevator negative power control system.As shown in Figure 5, hoisting crane is to comprise with second kind of optional structure of the open-circuit system 3 in the enclosed elevator negative power control system: open type controllable capacity pump 30, be connected with auxiliary gear box 2, and be used for obtaining power and pressure oil output from auxiliary gear box 2; Solenoid directional control valve 51; Pilot operated directional control valve 52; Ratio loads by pass valve 53.Open type controllable capacity pump 30, solenoid directional control valve 51 and ratio load by pass valve 53 and are connected with pilot operated directional control valve 52 respectively; Solenoid directional control valve 51 is used to control the conducting of pilot operated directional control valve 52 or turn-off.In structure shown in Figure 5; Solenoid directional control valve 51 can be controlled the switching of pilot operated directional control valve 52 mode of operations; To realize that pressure oil and ratio load the by pass valve disconnection and perhaps be communicated with, the size of passing ratio loading by pass valve 53 control loaded pressure realizes the step-less adjustment of on-load pressure.
Fig. 6 is according to the hoisting crane of the embodiment of the invention the third basic structure scheme drawing with enclosed elevator negative power control system.As shown in Figure 6, hoisting crane is to comprise with the third optional structure of the open-circuit system 3 in the enclosed elevator negative power control system: open type controllable capacity pump 30, be connected with auxiliary gear box 2, and be used for obtaining power and pressure oil output from auxiliary gear box 2; First proportional reversing valve 621 and second proportional reversing valve 622 all are connected with open type controllable capacity pump 30; First to fourth guide proportion reducing valve 611 to 614, wherein the first and second guide proportion reducing valves 611,612 are connected with first proportional reversing valve 621, and the third and fourth guide proportion reducing valve is connected with second proportional reversing valve 622; The amplitude oil cylinder 63 of hoisting crane and loading by pass valve 64; Wherein the rodless cavity of amplitude oil cylinder 63 is connected with second proportional reversing valve 622 with first proportional reversing valve 621; The rod chamber of amplitude oil cylinder 63 is connected with first proportional reversing valve 621, loads by pass valve 64 and is connected with second proportional reversing valve 622.Amplitude oil cylinder 63 can absorb the power that open type controllable capacity pump 30 is obtained.The first guide proportion reducing valve 611 is used for control presssure oil flows to first hydraulic fluid port of amplitude oil cylinder 63 via first proportional reversing valve 621 flow; The second guide proportion reducing valve 612 is used for control presssure oil flows to second hydraulic fluid port of amplitude oil cylinder 63 via first proportional reversing valve 621 flow; The 3rd guide proportion reducing valve 613 is used for control presssure oil flows to first hydraulic fluid port of amplitude oil cylinder 63 via second proportional reversing valve 622 flow; The 4th guide proportion reducing valve 614 is used for control presssure oil and flows to the flow that loads by pass valve 64 via second proportional reversing valve 622.In Fig. 6, be rodless cavity in first hydraulic fluid port of amplitude oil cylinder 63, be rod chamber in second hydraulic fluid port.
Below the technical scheme of present embodiment is described further.
Enclosed controllable capacity pump 31 is formed the closed system working connection with hoist motor 32, provides kinetic energy to promote weight G to hoisting speed reducer 33, and in weight G decline process, its potential energy converting and energy is that kinetic energy passes to closed system.Driving engine is had an effect through auxiliary gear box and open-circuit system (through directly acting on the open type controllable capacity pump) and closed system (through directly acting on the enclosed controllable capacity pump) simultaneously.Auxiliary gear box is as an energy delivery mechanisms: it can pass to the power of driving engine output simultaneously the open type controllable capacity pump and realize externally doing work with the enclosed controllable capacity pump; The negative power (the enclosed controllable capacity pump drives auxiliary gear box and turn of engine under this operating mode) that produces in the time of also can weight in the closed system being descended passes to auxiliary gear box, passes to driving engine and open-circuit system through auxiliary gear box.
The main operation element of closed system is enclosed controllable capacity pump and hoist motor.The enclosed controllable capacity pump is responsible for controlling the speed control that hoisting mechanism hoists and descends, and hoist motor is connected with reductor, is synchronized with rising and falling of weight.When weight hoisted, driving engine was input to the enclosed controllable capacity pump through auxiliary gear box with portion of energy, and this moment, driving engine externally did work, and weight is raised.When weight descended, the weight by gravity drove winch and rotates, thereby drove hoist motor and the rotation of enclosed controllable capacity pump, and the enclosed controllable capacity pump is given auxiliary gear box with transfer of energy.This decline process is that the enclosed controllable capacity pump is to auxiliary gear box and driving engine acting.Therefore this is a negative power (this operating mode of driving engine is external horsepower output, but absorbed power) and the energy that driving engine absorbs is limited for driving engine.
The negative power P that produces when weight descends
mFor:
P
m＝M×g×V…………(1)
In the formula (1): M representes the lift heavy quality; G representes acceleration due to gravity; V representes the weight descending speed.
The negative power that is delivered to closed system is P
cFor:
P
c＝M×g×V×η
1×η
2…………(2)
In the formula (2): η
1The mechanical efficiency of expression reductor and wire rope pulley group; η
2The mechanical efficiency of expression hydraulic efficiency pressure system.
The negative power P that driving engine absorbs
e=P
c, i.e. P
e=M * g * V * η
1* η
2(3)
P in the formula
eExpression driving engine absorbed power.
Can find out that from formula (3) negative power that driving engine absorbs is directly proportional with the mass M of weight, V is directly proportional with descending speed.And the absorbable negative power of driving engine is limited, and therefore when hoisting capacity M increased, the maximum falling speed V of weight then should reduce.Along with the development of hoisting crane, the increase of hoisting capacity only absorbs negative power by driving engine and can not satisfy the demands.
The negative power that weight decline produces is absorbed by driving engine and open-circuit system.Wherein the driving engine power absorbed is:
P
e＝P
c-P
k…………(4)
In the formula: P
kThe negative power that the expression open-circuit system absorbs.
Draw the negative power that driving engine absorbs: P thus
e=MgV * η
1* η
2-P
k(5)
The negative power P that present embodiment absorbs through the control open-circuit system
k, realize the negative power P that driving engine absorbs
eLess than its absorbable maximum negative power P
e≤P
Em(P wherein
EmThe absorbable maximum negative power of expression driving engine).
Below be the working process of the enclosed elevator negative power control system in the example explanation present embodiment with Fig. 6.
In Fig. 6, the A2 mouth of the A1 mouth of first proportional reversing valve 621 and second proportional reversing valve 622 collaborates the rodless cavity fuel feeding to amplitude oil cylinder; The B1 mouth of first proportional reversing valve 621 is amplitude oil cylinder 63 rod chamber fuel feeding; The B2 mouth of second proportional reversing valve 622 is that ratio loads by pass valve 64 fuel feeding; The meta function of second proportional reversing valve 622 is " O " type function.Concrete control is as follows: when guide's proportional pressure-reducing valve 611,612,613 and 614 whole dead electricity, first proportional reversing valve 621, second proportional reversing valve 622 are in meta, and system does not have pressure oil and exports; When guide's proportional pressure-reducing valve 611 first proportional reversing valve 621 is in the work of right position when electric, pressure oil gets into amplitude oil cylinder 63 rodless cavities through first proportional reversing valve 621 from the A1 mouth, amplitude oil cylinder 63 realizes hoisting action; When guide's proportional pressure-reducing valve 612 when electric, first proportional reversing valve 621 is in the work of position, a left side, pressure oil gets into amplitude oil cylinder 63 rod chambers through first proportional reversing valve from the B1 mouth, luffing is realized down maneuver; When guide's proportional pressure-reducing valve 611,613 simultaneously when electric, pressure oil advances the luffing rodless cavity through first proportional reversing valve 621 from the A1 mouth, pressure oil advances the luffing rodless cavity through second proportional reversing valve 622 from the A2 mouth simultaneously, the high speed interflow when having realized amplitude-variation hoisting; When guide's proportional pressure-reducing valve 614 when electric, pressure oil advances ratio through second proportional reversing valve 622 from the B2 mouth and loads by pass valve 64.The control presssure of guide proportion reducing valve 611 to 614 outputs is proportional to control current among the figure; Therefore can realize the ratio output of first proportional reversing valve 621 and second proportional reversing valve, 622 flows, thereby realize that the speed of amplitude oil cylinder or the flow that ratio loads by pass valve are directly proportional with received current.
The negative power that open-circuit system absorbs is made up of two parts, the power that consumes when a part is moved for changing-breadth system, and a part is for loading the power that consumes when by pass valve loads.Wherein the power of changing-breadth system consumption is operating mode decision in the hoisting process (whether move such as amplitude oil cylinder, the speed of action is that the requirement by actual condition determines), and the power of loading system to be us can control in real time, be a variable parameter.
P
K＝Q
1×ΔP
1/600+Q
2×ΔP
2/600…………(6)
In the formula: Q
1The flow of expression changing-breadth system; Δ P
1Expression changing-breadth system pressure; Q
2Expression is supplied with and is loaded the by pass valve flow; Δ P
2Expression loads by pass valve pressure;
Draw thus:
P
e＝MgV×η
1×η
2-Q
1×ΔP
1/600-Q
2×ΔP
2/600…………(7)
The power output state of driving engine itself can be drawn by the monitoring in real time of its controller that carries, and passes to peripheral control system through the CAN bus, and we are called the engine loading rate.Engine loading rate=driving engine real output/engine rated power.Exist under the situation of negative power, generally keep the engine loading rate in a fixed value (such as 5%), we regard it as target control value.
When load factor is lower than expected value, increase the control current of guide proportion reducing valve 614, export to the flow (Q in the formula (7) that ratio loads by pass valve with the scaling up change-over valve
2) make ratio loading by pass valve consumed power increase, impel the engine loading rate to return to expected value; Otherwise when the engine loading rate is higher than expected value, can reduce the electric current of guide proportion reducing valve 614,, make the engine loading rate maintain expected value to reduce to load the consumption of power of by pass valve.
In addition, for system shown in Figure 5, when load factor was lower than expected value, scaling up loaded the received current of by pass valve 53, loaded on-load pressure (the Δ P in the formula (7) of by pass valve with scaling up
2) make ratio loading by pass valve consumed power increase, impel the engine loading rate to return to expected value; Otherwise when the engine loading rate is higher than expected value, can reduce the received current that ratio loads by pass valve 53,, make the engine loading rate maintain expected value to reduce to load the consumption of power of by pass valve.
Adopt electricity liquid ratio relief valve like the loading by pass valve in the present embodiment, then its pressure size (Δ P in the formula (7)
2) can realize stepless control through the size of regulating its control current.When load factor is low, can make control current less relatively, make that the overshoot when by pass valve is opened reduces, load more steady.
Through above system and control method, the negative power that is input to driving engine when the enclosed elevator is transferred is no more than its absorbable maxim.No matter how hoisting capacity M and descending speed V change, all can be through electric guide proportion reducing valve 614 or ratio being loaded the real-time control of by pass valve 53 size of current, and the driving engine that makes absorbs negative power and maintains the goal-setting value.
Can find out from above description, use the technical scheme of present embodiment, can obtain following beneficial effect:
The negative power that is produced when 1, the enclosed elevator descends is delivered to open-circuit system by auxiliary gear box, is absorbed by open-circuit system, and the weight descending speed no longer is restricted;
2, realize that through the electric current of control guide proportion reducing valve proportional reversing valve exports to the flow proportional control that ratio loads by pass valve; Load the different loading power of by pass valve to obtain ratio; Owing to be controlled to be step-less adjustment, therefore load and stablize, can not make speed produce sudden change;
But 3, the ratio also step-less adjustment of pressure that loads by pass valve, the low system overshoot of hour setting pressure is little for the negative power that produces in closed system, loads more steadily, and the negative power that produces when closed system is greatly the time, the higher satisfied loading power requirement of setting pressure;
4, no matter how the negative power of closed system output changes, electric current that all can be through control guide proportion reducing valve/or the electric current that ratio loads by pass valve make the power of driving engine maintain target control value;
5, second proportional reversing valve 622 can be realized amplitude-variation hoisting and two functions of system loads, and more traditional mode has been saved a proportional reversing valve.
Obviously, it is apparent to those skilled in the art that above-mentioned each module of the present invention or each step can realize with the general calculation device; They can concentrate on the single computer device; Perhaps be distributed on the network that a plurality of computer device forms, alternatively, they can be realized with the executable program code of computer device; Thereby; Can they be stored in the memory storage and carry out, perhaps they are made into each integrated circuit modules respectively, perhaps a plurality of modules in them or step are made into the single integrated circuit module and realize by computer device.Like this, the present invention is not restricted to any specific hardware and software combination.
The above is merely the preferred embodiments of the present invention, is not limited to the present invention, and for a person skilled in the art, the present invention can have various changes and variation.All within spirit of the present invention and principle, any modification of being done, be equal to replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (10)
1. a hoisting crane is with enclosed elevator negative power control system, is used to absorb the negative power that the hoisting mechanism of hoisting crane produces when the lift heavy thing is transferred, and it is characterized in that said control system comprises driving engine, auxiliary gear box, open-circuit system and closed system, wherein:
Said open-circuit system is connected with said auxiliary gear box respectively with closed system, and is connected to said driving engine through said auxiliary gear box;
Said closed system comprise with said auxiliary gear box bonded assembly enclosed controllable capacity pump, through hydraulic tubing and said enclosed controllable capacity pump bonded assembly hoist motor and with said hoist motor bonded assembly hoisting speed reducer;
Said auxiliary gear box is used for when hoisting crane descends operation said negative power partly or entirely passed to said open-circuit system.
2. control system according to claim 1 is characterized in that, comprises in the said open-circuit system:
The open type controllable capacity pump is connected with said auxiliary gear box, is used for obtaining power and pressure oil output from said auxiliary gear box;
Proportional reversing valve is connected with said open type controllable capacity pump;
The loading by pass valve of said hoisting crane is connected with said proportional reversing valve;
The guide proportion reducing valve is connected with said proportional reversing valve, is used to control said pressure oil flows to said loading by pass valve via said proportional reversing valve flow.
3. control system according to claim 1 is characterized in that, comprises in the said open-circuit system:
The open type controllable capacity pump is connected with said auxiliary gear box, is used for obtaining power and pressure oil output from said auxiliary gear box;
Pilot operated directional control valve is connected with said open type controllable capacity pump;
Ratio loads by pass valve, is connected with said pilot operated directional control valve;
Solenoid directional control valve is connected with said pilot operated directional control valve, is used to control the conducting of said pilot operated directional control valve or turn-off.
4. control system according to claim 1 is characterized in that, comprises in the said open-circuit system:
The open type controllable capacity pump is connected with said auxiliary gear box, is used for obtaining power and pressure oil output from said auxiliary gear box;
First and second proportional reversing valves all are connected with said open type controllable capacity pump;
First to fourth guide proportion reducing valve, wherein the first and second guide proportion reducing valves are connected with first proportional reversing valve, and the third and fourth guide proportion reducing valve is connected with second proportional reversing valve;
Hydraulic Elements and loading by pass valve, first hydraulic fluid port of wherein said Hydraulic Elements is connected with said first and second proportional reversing valves, and second hydraulic fluid port is connected with said second proportional reversing valve, and said loading by pass valve is connected with said second proportional reversing valve; And,
Said Hydraulic Elements are used to absorb the power that said open type controllable capacity pump is obtained;
The said first guide proportion reducing valve is used to control said pressure oil flows to first hydraulic fluid port of said Hydraulic Elements via said first proportional reversing valve flow;
The said second guide proportion reducing valve is used to control said pressure oil flows to second hydraulic fluid port of said Hydraulic Elements via said first proportional reversing valve flow;
Said the 3rd guide proportion reducing valve is used to control said pressure oil flows to first hydraulic fluid port of said Hydraulic Elements via said second proportional reversing valve flow;
Said the 4th guide proportion reducing valve is used to control said pressure oil flows to said loading by pass valve via said second proportional reversing valve flow.
5. control system according to claim 4 is characterized in that, said loading by pass valve is that ratio loads by pass valve.
6. according to claim 4 or 5 described control system, it is characterized in that said Hydraulic Elements are the HM Hydraulic Motor of two plate valves interflow control or the telescopic oil cylinder of two plate valves interflow control.
7. according to claim 4 or 5 described control system, it is characterized in that said Hydraulic Elements are the amplitude oil cylinder of said hoisting crane, said first hydraulic fluid port is the rodless cavity of this amplitude oil cylinder, and said second hydraulic fluid port is the rod chamber of this amplitude oil cylinder.
8. control system according to claim 7 is characterized in that, said amplitude oil cylinder is two amplitude oil cylinder.
9. according to the described control system of claim 2,3 or 4, it is characterized in that said open type controllable capacity pump is load sensing pump or automatically controlled controllable capacity pump.
10. a hoisting crane is characterized in that, comprises that each described hoisting crane is with enclosed elevator negative power control system in the claim 1 to 9.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110412215.0A CN102491173B (en) | 2011-12-12 | 2011-12-12 | Crane and closed type winch negative power control system for crane |
| PCT/CN2012/082075 WO2013086882A1 (en) | 2011-12-12 | 2012-09-26 | Crane, and closed-type hoist negative power control system for use with crane |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110412215.0A CN102491173B (en) | 2011-12-12 | 2011-12-12 | Crane and closed type winch negative power control system for crane |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102491173A true CN102491173A (en) | 2012-06-13 |
| CN102491173B CN102491173B (en) | 2014-04-02 |
Family
ID=46183044
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110412215.0A Active CN102491173B (en) | 2011-12-12 | 2011-12-12 | Crane and closed type winch negative power control system for crane |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN102491173B (en) |
| WO (1) | WO2013086882A1 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013086882A1 (en) * | 2011-12-12 | 2013-06-20 | 中联重科股份有限公司 | Crane, and closed-type hoist negative power control system for use with crane |
| CN103350955A (en) * | 2013-07-25 | 2013-10-16 | 中联重科股份有限公司 | Crane, negative power system, negative power control method, and negative power control apparatus |
| CN103832314A (en) * | 2012-11-26 | 2014-06-04 | 徐州徐工随车起重机有限公司 | Road wrecker with U-type hanging arm |
| CN108212335A (en) * | 2017-12-27 | 2018-06-29 | 徐工集团工程机械有限公司 | Crusher |
| CN110925252A (en) * | 2019-11-18 | 2020-03-27 | 中联重科股份有限公司 | Integrated multi-way valve, lifting hydraulic control system and crane |
| CN113582024A (en) * | 2021-06-17 | 2021-11-02 | 中联重科股份有限公司 | Negative power control method, equipment and system for crane and crane |
| CN113879995A (en) * | 2021-09-14 | 2022-01-04 | 徐州徐工基础工程机械有限公司 | Main winch variable load lowering control method and rotary drilling rig |
| CN113914173A (en) * | 2021-10-29 | 2022-01-11 | 柳工无锡路面机械有限公司 | Hydraulic control system of paver screed plate |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3864915A (en) * | 1972-07-28 | 1975-02-11 | Richier Sa | Hydraulic system for displacing a load with automatic hydrostatic balancing |
| WO1996036554A1 (en) * | 1995-05-19 | 1996-11-21 | Tamrock Oy | An arrangement for controlling a winch of a rock drilling equipment |
| US6079576A (en) * | 1995-12-13 | 2000-06-27 | Liebherr-Werk Ehingen Gmbh | Control device for a hoist mechanism of a crane |
| EP1118580A1 (en) * | 2000-01-21 | 2001-07-25 | LEITNER S.p.A. | Device for automatic tension control of a cable for a piste grooming device |
| CN101723271A (en) * | 2008-10-15 | 2010-06-09 | 徐州重型机械有限公司 | Hydraulic control system for crane hoisting |
| CN201873475U (en) * | 2010-06-30 | 2011-06-22 | 徐工集团工程机械股份有限公司建设机械分公司 | Control system for hydraulic motor of winding system |
| FR2956105A1 (en) * | 2010-02-10 | 2011-08-12 | Payant Ets | Traction device i.e. hauler, for use at rear side of haulage tractor, has frame deformation sensor measuring tractive force exerted by cable, and tractive force regulation loop regulating tractive force according to deformation of frame |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4455770A (en) * | 1980-04-14 | 1984-06-26 | Presley Glen T | Trencher power control system |
| JPH09278371A (en) * | 1996-04-17 | 1997-10-28 | Keisuke Shigemitsu | Power source selectable mobile crane |
| DE19824319A1 (en) * | 1998-06-02 | 1999-12-16 | O & K Mining Gmbh | Method for regulating in particular the swiveling device of a mobile machine |
| US6994223B1 (en) * | 2002-10-29 | 2006-02-07 | Auto Crane Company | Diagnostic readout for operation of a crane |
| CN101850937B (en) * | 2010-04-13 | 2012-06-13 | 中国一冶集团有限公司 | Closed hydraulic circuit of hoisting winding engine |
| CN201729582U (en) * | 2010-04-13 | 2011-02-02 | 中国一冶集团有限公司 | Closed hydraulic oil way of hoister |
| CN102491173B (en) * | 2011-12-12 | 2014-04-02 | 中联重科股份有限公司 | Crane and closed type winch negative power control system for crane |
-
2011
- 2011-12-12 CN CN201110412215.0A patent/CN102491173B/en active Active
-
2012
- 2012-09-26 WO PCT/CN2012/082075 patent/WO2013086882A1/en active Application Filing
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3864915A (en) * | 1972-07-28 | 1975-02-11 | Richier Sa | Hydraulic system for displacing a load with automatic hydrostatic balancing |
| WO1996036554A1 (en) * | 1995-05-19 | 1996-11-21 | Tamrock Oy | An arrangement for controlling a winch of a rock drilling equipment |
| US6079576A (en) * | 1995-12-13 | 2000-06-27 | Liebherr-Werk Ehingen Gmbh | Control device for a hoist mechanism of a crane |
| EP1118580A1 (en) * | 2000-01-21 | 2001-07-25 | LEITNER S.p.A. | Device for automatic tension control of a cable for a piste grooming device |
| CN101723271A (en) * | 2008-10-15 | 2010-06-09 | 徐州重型机械有限公司 | Hydraulic control system for crane hoisting |
| FR2956105A1 (en) * | 2010-02-10 | 2011-08-12 | Payant Ets | Traction device i.e. hauler, for use at rear side of haulage tractor, has frame deformation sensor measuring tractive force exerted by cable, and tractive force regulation loop regulating tractive force according to deformation of frame |
| CN201873475U (en) * | 2010-06-30 | 2011-06-22 | 徐工集团工程机械股份有限公司建设机械分公司 | Control system for hydraulic motor of winding system |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013086882A1 (en) * | 2011-12-12 | 2013-06-20 | 中联重科股份有限公司 | Crane, and closed-type hoist negative power control system for use with crane |
| CN103832314A (en) * | 2012-11-26 | 2014-06-04 | 徐州徐工随车起重机有限公司 | Road wrecker with U-type hanging arm |
| CN103350955A (en) * | 2013-07-25 | 2013-10-16 | 中联重科股份有限公司 | Crane, negative power system, negative power control method, and negative power control apparatus |
| CN108212335A (en) * | 2017-12-27 | 2018-06-29 | 徐工集团工程机械有限公司 | Crusher |
| CN110925252A (en) * | 2019-11-18 | 2020-03-27 | 中联重科股份有限公司 | Integrated multi-way valve, lifting hydraulic control system and crane |
| CN113582024A (en) * | 2021-06-17 | 2021-11-02 | 中联重科股份有限公司 | Negative power control method, equipment and system for crane and crane |
| CN113879995A (en) * | 2021-09-14 | 2022-01-04 | 徐州徐工基础工程机械有限公司 | Main winch variable load lowering control method and rotary drilling rig |
| CN113914173A (en) * | 2021-10-29 | 2022-01-11 | 柳工无锡路面机械有限公司 | Hydraulic control system of paver screed plate |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102491173B (en) | 2014-04-02 |
| WO2013086882A1 (en) | 2013-06-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102491173B (en) | Crane and closed type winch negative power control system for crane | |
| CN103244496B (en) | Rotary control valve group, revolution hydraulic control system and hoist | |
| CN104163385B (en) | A kind of winch hydraulic control system | |
| CN200974743Y (en) | Energy-saving tower machine hydraulic stepless change control system | |
| CN202643158U (en) | Constant tension hoisting operation wave compensation device | |
| CN103922235A (en) | Deep-sea winch wave compensation hydraulic driving system with load adaptability | |
| CN203319595U (en) | Crane hoisting hydraulic system and crane | |
| CN102887447A (en) | Hydraulic control loop of variable amplitude hydraulic cylinder, crane and variable amplitude control method | |
| CN202988618U (en) | Closed hydraulic circuit for controlling boom rotation and crane | |
| CN101857174B (en) | Hydraulic system of mechanically operated triple pump | |
| CN110778551B (en) | Full-closed hydraulic system of crane | |
| CN101230870A (en) | Flow-control module of crane executing mechanism | |
| CN101863421B (en) | Hydraulic operation triple pump hydraulic system | |
| CN101863420A (en) | Hydraulically operated four-pump hydraulic system | |
| CN113323930B (en) | Multistage pressure control and pressure speed regulation hydraulic system and operation machinery | |
| CN102146943A (en) | Motor pressure turn-off control system and crane applying same | |
| CN208330867U (en) | A kind of distributed direct drive excavator hydraulic system of servo motor driving bivariate pump | |
| CN201729582U (en) | Closed hydraulic oil way of hoister | |
| CN202054561U (en) | Hydraulic closed-type constant tension device | |
| CN101850937A (en) | Closed hydraulic circuit of hoisting winding engine | |
| CN103307045A (en) | Hydraulic system and crane | |
| CN101857173B (en) | Hydraulic system of mechanically operated quadruple pump | |
| CN203627359U (en) | Crane for foundation pile construction and hydraulic system thereof | |
| CN201670659U (en) | Hydraulic control operation triple-pump hydraulic system | |
| CN105889160B (en) | Steel scrap cuts quick hydraulic system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |